Paper feed mechanism

ABSTRACT

A twin cylinder stencil duplicating machine including a corner separator paper feed mechanism having a single knob adjustment for establishing different degrees of interference for various paper stocks and operating conditions such as machine speed.

W tates Patent 1151 3,652,083 0583mm [451 Mar. 28, 1972 [54] PAPER FEED MECHANISM 3,288,460 11/1966 Eichorn ..271/l9 3,294,019 12/1966 Taylor .271/40X [72] Invent Bmmd" 3,369,804 2/1968 Schulze et a1 ..271/21 [73] Assignee: John Benton Inc., Mineola, N.Y.

Primary Examiner-Joseph Wegbreit [22] filed 1969 Attorney-Amster & Rothstein [21] Appl. No.: 873,042

[57] ABSTRACT [52] US. Cl ..27 1/39, 271/53 A in'cylinder Stencil duplicating machine including a comer [51] Int. Cl ..B65h 3/06 Separator P p feed mechanism having a Single knob 1 [5 3] Field f S h 271/36, 39, 40, 41 5 3, 62, ment for establishing different degrees of interference for vari- 271/19, 21 ous paper stocks and operating conditions such as machine speed. 56 Rafe e Cited 1 ms 26 Claims, 21 Drawing Figures UNITED STATES PATENTS A 3,214,165 10/1965 Warner..... 211 2 7 r PATENTEDMARZB I972 SHEET OZUF 10 .i ii ii,.zEiiL mvENfoR WILL/AIM Bow/M RD? ATTOR NEYS PATENTEDMme I872 SHEET OBUF 10 INVENTOR WILL/AM Boss/MRO? BY g ATTORNEYS PATENTEDMARZBIQIE 3.652.083

- sum sum 10 INVENTOR WILL/AM BOSSA/A R07 MHz/114a ATToRNEYs ,P'ATENTEnmARzs m2 SHEET OSUF -10 INVENTOR W/ll/AM BQSSHARDT ATTQRNEYS Mzm PMFNFYED MAR 2 8 1972 sum OBUF 10 www WW ORNEYS PATENTEDMRBB m2 V 3.652.083

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w a B F ATT'ORNEYS PAPER FEED MECHANISM The present invention relates generally to printing machines, and in particular, to a twin cylinder stencil duplicator for printing from a stencil master.

Among the equipments available for producing relatively large numbers of copies at relatively low cost are the so-called single cylinder and twin cylinder stencil duplicators, also known as mimeograph machines. In the typical single cylinder machine, there is provided a hollow inking drum which is perforated in its cylindrical surface and provided with an ink pad through which ink penetrates through a stencil mounted on the drum to the paper sheets as they are fed. The second type is the twin cylinder stencil duplicator in which two cylinders are mounted in spaced parallel relation around which a silk screen stencil carrier is mounted. Provision is made for applying a sufficient amount of ink to the surface of the cylinders for transfer to the copy paper through the silk screen and through the stencil during the printing function.

Twin cylinder stencil duplicators can use a viscous paste ink which tends not to leak and produces good quality mimeograph copies. They can be operated by untrained office personnel with little instruction. The fully automatic stencil duplicators that minimize the skills required by the operator have steadily become more complex mechanically and, pari passu, more expensive until in some cases they approach the cost of offset duplicators. However, if it were possible to provide a twin cylinder duplicator of simplified design and comparatively low cost which was easy to operate and could produce good quality copies with minimum operative complexity and servicing requirements, such a machine would find broad acceptance.

Accordingly, it is an object of the present invention to provide a twin cylinder stencil duplicator which realizes one or more of the aforesaid objectives. Specifically, it is within the contemplation of the invention to provide a twin cylinder stencil duplicator which provides all the functional, sensing and control features for machines of this type, yet is of relatively simple construction and is capable of mass production manufacture at a relatively low unit cost.

It is a further object of the invention to provide an improved duplicating machine of this type which incorporates the requisite convenience features for rapid, good quality duplicating yet is sufficiently simple for unskilled personnel to operate easily.

One of the problems in office duplicating machines is to provide a reliable and trouble-free paper feed, that is, a feed that separates successive sheets in the stack for feeding one at a time to the printing mechanisms. One method for accomplishing sheet separation involves the provision of comer separators which exert an interference to separate the top sheet from the paper stack. Typically, such comer separators are not adjustable to accommodate different paper weights and machine speeds. In other cases, it is necessary to substitute different pairs of corner separators of varying interference to properly feed the various paper stocks printed. Operation is therefore inconvenient and troublesome.

In accordance with the present invention, an improved corner separator feed is provided whereby a simple manual manipulation, such as turning a control knob, automatically adjusts the corner separators for various types of paper and operating conditions. In accordance with this aspect of the invention, there is provided, in a printing machine, a feed tray for supporting a stack of sheets which includes adjustable left and right side guides which are movable relative to each other in accordance with the width of the paper stack. Left and right corner separators are mounted independently of the side guides but for movement with and relative to the left and right side guides, respectively. The left and right corner separators are movable in response to the adjustment of the left and right side guides. Once the left and right side guides are set in their adjusted positions, further actuating means are provided for simultaneously adjusting the left and right corner separators relative to, but independently of, the left and right side guides for obtaining an independent adjustment of the interference provided by the left and right corner separators in any adjusted position of the left and right side guides. Accordingly, a stack of paper may be loaded into the machine and the left and right side guides adjusted laterally to confine the stack. Thereupon, and by a simple manual manipulation of the actuating means, the requisite corner separator interference can be established for the particular paper stock and feeding conditions, and virtually foolproof sheet-by-sheet feeding obtained for machine operation at all speeds.

As a further feature of the invention, provision is made for the varying operative speed from as slow as 60 copies per minute to as fast as copies per minute and to provide the requisite ink supply for all machine speeds and copy characteristics. Ink feeding requirements vary as a function of copying speed, type of paper being printed and the degree of ink coverage for the copy being duplicated. Advantageously, the present machine incorporates an automatic inking system which is much less complicated than comparable systems on existing twin cylinder equipments, is reliable and trouble-free in operation and is readily adjusted by the operator to provide the amount of ink required. In accordance with this aspect of the invention, the machine includes a movable ink stand having a disposable sealed ink container mounted thereon. An indexing mechanism is operatively connected to the stand for effecting step-by-step movement of the ink container against its cover which acts as a piston, to supply ink in discrete amounts. Actuating mechanisms, including motion accumulating means, are operatively connected to the indexing mechanism and are operative in response to a predetermined and preset number of revolutions of the main shaft of the machine for imparting an indexing stroke to the index mechanism to effect ink dispensation. By a simple manual adjustment, the operator can preset the automatic inking mechanism to deliver more or less ink to the printing mechanisms in accordance with various printing requirements. Altemately, the automatic inking can be disengaged and ink provided by a hand-operated lever.

As a still further aspect of the invention, the machine incorporates all of the requisite operating features, sensing, and control functions, yet is a highly simplified mechanical design in which parts and functions are combined to reduce the total number of parts and to achieve relative machine simplicity. In accordance with this aspect of the present invention, the printing machine includes the usual printing mechanisms, paper feed and receiving tray assemblies and paper feeding mechanisms. A unified drive is provided for such mechanisms which includes a main drive shaft having a series of cams and followers associated therewith arranged to establish a coordinated and timed relationship in the actuation of the paper feeding, paper registration, and printing mechanisms.

As a further feature of the present invention, the machine is designed such that it may be initially equipped either for manual operation or motorized operation. Unlike other stencil duplicators, the machine may be readily converted in the field through a motor kit from a manually operated machine to a motor-driven machine. In accordance with this aspect of the invention, a hand-driven crank is provided for the drive shaft of the unified drive and means are provided for releasably coupling the crank to the drive shaft for manual operation. A motor drive is provided which includes a single support which is releasably attached to the machine frames, which single sup port serves as a mount for an electrical motor with appropriate gearing, clutch and connecting means which engage the motor to the drive shaft when the support is mounted to the frame of the machine. The subassembly of the support, including the motor, the associated connecting means, controls and wiring, are attachable and removable from the machine as a unit whereby any hand-operated machine may be motorized simply by attaching the motor support to the machine frames. Conveniently, the single support is also one of the external cover panels so that the requisite motor controls and wiring needed for motorized operation are in their appropriate operating locations.

The above brief description, as well as further objects, features and advantages of the present invention will be more fully appreciated by reference to the following detailed description of a presently preferred, but nonetheless illustrative embodiment demonstrating the several features and advantages of the present invention, when taken in conjunction with the accompanying drawing, wherein:

FIG. I is a front elevational view of an improved duplicating machine embodying features of the present invention, with some parts broken away;

FIG. 2 is a diagrammatic view taken longitudinally through the machine and showing the relationship of the paper feeding and paper control mechanisms at the start of paper feed;

FIG. 3 is a view similar to FIG. 2 but further advanced in the paper-feeding cycle;

FIG. 4 is a medial sectional view, on an enlarged scale, taken substantially along the line 44 ofFlG. 1 and looking in the direction of the arrow;

FIG. 5 is an elevational view taken from the left of FIG. 1 as indicated by the directional arrow, with the left cover removed and the front and rear covers swung to their respective open positions and showing the mechanisms mounted on the left side plate of the machine;

FIG. 6 is an enlarged elevational view similar to FIG. 5 but with parts removed for clarity;

FIG. 7 is a plan view, on a reduced scale and with parts broken away, showing the feed tray and associated mechanisms of the machine;

FIG. 8 is a bottom plan view of the feed tray and related mechanisms, with parts broken away;

FIG. 9 is an enlarged detail of a portion of the positioning mechanisms for the corner separators which is on the underside of the feed tray;

FIG. 10 is a fragmentary plan view, on an enlarged scale and with parts broken away, showing part of the feed tray and the related corner separator mechanism;

FIG. 11 is a sectional view taken substantially along the line ll 11 of FIG. 7, on an enlarged scale;

FIG. 12 is an elevational view of the right side of the machine taken along the directional arrow 12 in FIG. 1, with the right side cover removed, with the front and rear covers shown respectively in their open positions and illustrating the mechanisms mounted on the outer side of the right side plate of the machine;

FIG. 13 is an enlarged fragmentary elevational view of a portion of FIG. 12, with the control mechanism shown in the operative or on position;

FIG. 14 is a view similar to FIG. 13, but showing the control mechanism in the inoperative or off position;

FIG. 15 is a sectional view, on an enlarged scale, taken substantially along the line 15l5 in FIG. 12;

FIG. 16 is an enlarged elevational view of a portion of the mechanisms shown in FIG. 12;

FIG. 17 is a sectional view taken substantially along the line l717 of FIG. 1, with parts broken away, showing the mechanisms mounted on the inner side of the right side plate ofthe machine;

FIG. 18 is a sectional view taken along the line 18l8 of FIG. 17 and looking in the direction ofthe arrows;

FIG. 19 is a fragmentary plan view, with parts in section showing details of the feed mechanisms which are generally illustrated in FIG. 1;

FIG. 20 is a sectional view, on an enlarged scale, taken substantially along the line 20-20 ofFIG. l9; and

FIG. 21 is a cam diagram for the machine.

Referring now specifically to the drawings, and in particular to FIGS. 1 to 6, the present duplicating machine, which is generally designated by the reference numeral 30, is seen to include a housing 32 having a pivoted front cover and paper feed tray assembly 34 (see FIG. 4), a pivoted rear cover and paperreceiving tray assembly 36, a removable left side cover 38 mounted to house the mechanisms supported on the left side plate 40 of the machine and a removable right side cover 42 mounted to house the mechanisms mounted on the right side plate 44 of the machine. Straddling the machine is a removable front top cover 45 which is mounted on the left and right side plates, as by easily disengaged machine screws. As seen best in FIG. 5 and as shown by the dotted lines and indicated by the respective directional arrows, the front cover and tray assembly 34 and the rear cover 36 may be swung to their respective closed positions wherein they cooperate with the remainder of the housing 32, including side covers 38, 42 and front top plate 45 to completely enclose the duplicating mechanism and to form a dust-proof case. The front cover and tray assembly 34 is pivotally mounted at opposite side pivots 46a, 46b (see FIG. 7) which in turn movably mounted on the frame of the machine (as will be subsequently described) such that assembly 34 may be swung to its horizontal and operative position. The rear cover 36 is directly pivoted on the frame of the machine at side pivots 48 and may be swung about its pivots to a horizontal position projecting rearwardly of the machine 30 in which position it serves as the receiving tray for the machine.

The front cover and feed tray assembly 34 is operable successively to deliver the topmost sheet from a paper stack along a predetermined feed path to the duplicating mechanisms of the machine. Preliminary to a consideration of the duplicating mechanisms, drive controls, etc., it will be helpful to understand the paper-feeding mechanisms which achieve precision feed, sheet by sheet, and function for a variety of paper widths, lengths and weights.

Assembly 34 includes a tray platform 50 which includes top platform wall 52 and bottom platform wall 54 which are spaced apart and define a mechanism-receiving housing H therebetween (see FIG. 8). Projecting upwardly from and movably mounted on platform 50 (which is horizontal in the operative position of the machine) are left and right paper guides or tray sides 56, 58 which are adjustable towards and away from each other in accordance with stack width to laterally position and guide the paper stack therebetween. The symmetrically disposed and adjustable tray sides 56, 58 respectively include upstanding guide flanges 56a, 58a and horizontal support flanges 56b and 58b, the latter overlying and resting against the top platform wall 52, as seen best in FIG. 7. Paper guides 56, 58 extend front to back of the machine, with the mounting flanges 56b, 58b thereof extending beyond the leading edge 50a of platform 50, as seen in FIG. 8, for a purpose to be subsequently described. The paper guides 56, 58 are mounted for lateral adjustment toward and away from each other by the provision in platform top wall 52 of aligned and transversely extending guideways 52a, 52b which receive respective lockable mounting and latching mechanisms 56c, 58c which are carried on the paper guides 56, 58 and are locked and released by levers 56d, 58d which are conventional.

Extending from side to side of the machine at a location spaced in the direction of feed from the tray platform 50 is a horizontal fixed feed table 60 along which the topmost sheets pass in succession to the duplicating mechanisms 62. Fixed feed table 60 is fixed to the opposite side plates 40, 44 of the machine in any appropriate fashion and is at a fixed level in relation to the duplicating mechanisms 62 for guiding the topmost sheets along the requisite feed path to the duplicating mechanisms 62.

Fixed to and depending from feed table 60 intermediate edge 60a of the feed table 60 and edge 50a of tray platform 50 is an upstanding stack-abutment wall 64 against which the leading end edges of the stack of paper stock S abuts when the feed tray is loaded (see FIGS. 4, 7, 10 and 11). The stackabutment wall 64 is mounted in spaced relation between edge 50a of tray platform 50 and edge 60a of feed table 60 such that it may serve as an unobstructed guide track for left and right corner separator assemblies 66, 68 which are of identical and mirror image construction and are symmetrically disposed relative to the longitudinal center line of the adjustable tray 50, and side guides 56, 58. In this illustrative embodiment,

stack-abutment wall 64 is provided with right angle mounting tabs 64a, 64b at its opposite ends which are secured to the opposite sides of the fixed feed table 60 (see FIG. 7). Additionally, further support may be provided for wall 64 along the longitudinal center line of the tray, provided that the same does not obstruct the adjustment of the corner separator assemblies 66, 68.

The corner separator assemblies 66, 68 are laterally adjustable in two ways: (1) together with, and (2) simultaneouslyand independently of the respective side guides 56, 58. At any adjusted position of the side guides 56, 58, the corner separator assemblies 66, 68 are independently adjustable to overlap the left and right front corners of paper stack S in varying amounts in order to provide adjustable interference at the front corners of the stack S to assure proper feed for different paper weights and stiffness, machine feed rate, etc. The corner separator assemblies 66, 68 are of identical and mirror construction and the adjustment independent of tray sides 56, 58 is made simultaneously. Accordingly, it will suffice to describe only comer separator assembly 66, with particular reference being made to FIGS. 7 to 11, inclusive.

Corner separator assembly 66 includes backup plate 66a which extends behind and in a plane parallel to stack-abutment wall 64 and an adjusting flange 66b which is C-shaped and extends above and below wall 64 and projects forwardly of wall 64 at right angles thereto. Adjusting flange 66b is engaged by actuating mechanisms which are mounted within the mechanism-receiving housing H of tray platform 50. The flange 66b is engaged when the front cover and tray assembly 34 is swung into its horizontal operative position, and disengaged when tray assembly 34 is closed. The corner separator assemblies 66, 68 remain on the guide track provided by stack-abutment wall 64 when the tray assembly 34 is swung to its closed position about pivot 46; and when the tray assembly 34 is again swung to its operative horizontal position, the actuating mechanisms once again engage the respective comer separator assemblies 66, 68. A triangular plate 660 extends horizontally over stack-abutment wall 64 and overlies the corresponding corner of the paper stack S to exert the requisite interference to separate and allow the top sheet to be fed while restraining the remainder of stack S, during machine operation. Backup plate 66a and actuating flange 66b define a longitudinally extending cutout which surround wall 64, with sufficient clearance being afforded such that plate 66c drops onto the upper edge of wall 64 when the stack is removed from therebeneath, with the entire separator assembly 66 being able to accommodate upwardly and downwardly with the stack such that plate 66c in use, normally rests against the topmost sheet and floats free of the guiding and supporting rail 64 (see FIG. 11).

Still further, the corner separator assembly 66 includes an inwardly projecting arm 66d which extends in the same plane as backup plate 66a and terminates in the right angle guided tab (see FIG. 11) provided with the square cutout 66f. Extending through cutout 66f of guide tab 66e and the corresponding cutout of the guide tab of corner separator as sembly 68 is a floating stabilizing bar 69 which assures that assemblies 66, 68 will move in coordination with each other and will not skew relative to each other. Stabilizing bar 69 is positioned beneath table 60 and behind wall 64 and terminates short of the opposite sides thereof to achieve a stabilizing function without interfering with the other machine components. The length of stabilizing bar 69 is appropriate to guide assemblies 66, 68 in their various positions required in the adjustment of side guides 56, 58.

The actuating mechanism which achieves both the overall adjustment of the corner separator assemblies 66, 68 in response to the adjustment of the tray sides 56, 58 and independent, vernier adjustment thereof in any adjusted position of the tray sides 56, 58 is disposed within housing H. The actuating mechanism includes left and right carrier plates 70, 72 and a common L-shaped vernier actuating member 74. Carrier plates 70, 72 extend in a common plane beneath top platform wall 52 and include connecting fingers 70a, 72a coupled to respective downwardly bent tabs 56c, 58c on the adjacent forwardly projecting ends of the mounting flanges 56b, 58b. Contiguous to their opposite ends, carrier plates '70, 72 are provided at their inner sides with guide fingers 70b, 72b which extend through the respective transverse guideways 52a, 52b in top platform wall 52 and are secured to the adjacent inner side edges of the mounting flanges 56b, 56b (see 70b in FIG. 7). Spaced from the guide fingers 70b, 72b at the same end of the carrier plates 70, 72 are guide studs 70c, 72c which are received in the respective transverse guideways 52a, 52b. Thus, upon release of the conventional mounting and latch mechanisms 56c, 580 by actuating pivoted levers or finger pieces 56d, 58d, tray sides 56, 58 may be moved and will con currently move the carrier plates 7 0, '72.

In turn, carrier plates 70, 72 have pivotally mounted thereon left and right double arm actuating levers or bell cranks 76, 78. Levers 76, 78 are pivoted at 76a, 78a and have forwardly projecting main actuating arms 76b, 78b terminat ing in bifurcated ends which respectively engage the left and right corner separator assemblies 66, 68 (see FIGS. 7 and 10). Levers 76, 78 have laterally projecting auxiliary arms 760, 7 8c which likewise terminate in bifurcated ends which engage the common actuating flange 74a on the actuating member 74. Springs 80, 82 serve to bias the actuating arms 76b, 78b in the counterclockwise and clockwise directions, respectively, about pivots 76a, 78a and also urge the bifurcated auxiliary arms 76c, 78c into a tensioned position against actuating flange or rail 74a. Thus, as tray sides 56, 58 move toward and away from each other, there will be corresponding movement of the carrier plates 70, 72 and adjustment of the corner separator assemblies 66, 68 via main actuating arms 76b, 78b. The second adjustment to comer separator assemblies 66, 68 is imparted independently of tray sides 56, 58 when actuating member 74 is moved toward and away from edge 50a of tray platform 50, as indicated by the double-headed arrow in FIG. 8 and by the progressive dot-showings of adjusted positions for flange 74a. As flange 74a is moved, simultaneous and opposite symmetrical adjustments will be imparted to actuating levers 76, 78 and corresponding independent, vernier adjustments of the comer separator assemblies 66, 68 are made. The common actuating member 74 is slidably mounted at three points by pins which are received in elongated angular disposed slots, such as pins 74b fixed to top platform wall 52 and received in elongated slots 74c in the lower left end of member 74 (see FIG. 9).

The desired adjustment motion may be imparted to the common actuating member 74 in any convenient fashion, as for example, by the provision of a pivoted vernier adjustment knob 84 on top platform wall 52 to one side thereof (see FIG. 7). Knob 84 has a middle position extending transversely of wall 52. Turning knob 84 counterclockwise achieves an independent, vernier adjustment of the corner separator assemblies 66, 68 toward each other to increase interference with top sheet. Upon turning knob 84 clockwise, the assemblies 66, 68 are correspondingly adjusted outwardly from each other to decrease interference with top sheet. Adjustment knob 64 includes finger piece 84a overlying wall 52 which is mounted on vertical pivot 84b carrying eccentric 84c (see FIG. 9) which is received within an elongated follower slot 74d formed in the actuating member 74. A holddown plate and spring 742 is mounted on member 74 and is engaged over pivot 84b and a retaining washer 84d. A conventional detent mechanism may be associated with vernier adjustment knob 84 to accurately establish adjusted positions. This mechanism may be designed with any number of discrete vernier adjustments or, if desired, may be provided with an infinite vernier adjustment over any selected range.

The cover and tray assembly 34 is mounted to be raised automatically while in its operative attitude, to present the topmost sheet of the paper stack S for feed through the machine from a substantially fixed level regardless of the height of paper stack 5. The mounting arrangement includes identical inverted L-shaped tray carriers 86, 88 (see FIGS. 1,4, 12, 17) disposed at the opposite sides of the machine inwardly of the left and right side plates 40, 44. Carrier 86 is mounted for vertical movement by the provision of at least two slide blocks 90a, 90b which are carried by the tray carrier 86 and are confined in aligned vertically extending guideways 40a, 40b formed in the left side plate 40 (see FIGS. 4 and In similar fashion, the right tray carrier 88 is supported on slide blocks 92a, 9211 which are confined in aligned vertical guideways 44a, 44b formed in the right side plate 44 (see FIGS. 12 and 17). Conveniently, the slide blocks may be fabricated of an appropriate lubric material such that they require no maintenance or lubrication.

The forwardly projecting arms of the respective tray carriers 86, 88 provide corresponding pivots 46a, 46b at opposite sides of the machine for the tray assembly 34.

Along their rearward edges, the vertically extending arms of the tray carriers 86, 88 are formed with respective racks 86a, 88a (see FIGS. 4 and 17) such that the tray assembly 34 may be raised and lowered through the provision of a pinion shaft 94 which extends from side to side of the machine and carries respective actuating pinions 96a, 9612 which engage racks 86a, 88a. Pinion shaft 94 may be extended at one side of the machine (i.e., at the right side of the machine) and provided with a turn knob for manual raising and lowering of the tray assembly 34. Reference will now be made to the mechanism for automatically raising the tray assembly 34.

Preliminary to the description of this particular mechanism which may be operated from the main drive of the machine, whether manually or motor drive, it will be helpful to understand the construction and arrangement of the main drive. The main drive includes a main shaft 98 which extends from side to side ofthe machine above the tray assembly 34 and forwardly of the duplicating mechanism 62, with the main shaft 98 being journalled in appropriate bearings on the opposite side plates 40, 44 of the machine. Main shaft 98 extends through the right side plate 44 and through the right side cover 42 and carries a disengageable handle 100. Additionally, main shaft 98 extends beyond left side plate 40 into the adjacent housing where it carries, in succession from plate 40 outwardly, idler-actuating cam 102, impression roller release cam 104, main drive gear 106 and second feed roller drive cam 108. In lieu of manual turning of the main shaft 98 by crank 100, provision is made for a motor to drive main drive gear 106. As seen in FIGS. 1 and 4, the motor and reduction gear assembly and related parts are all on front top plate 45 and coupled by obvious reduction and coupling arrangements 112, 114, 116, 118, 120 and 122 to driving pinion 124 engaging main drive gear 105. Clutch 126 is provided such that the motor 110 and reduction gears are effectively decoupled from the main drive and main shaft 98 when the machine is turned by crank 100.

The machine may be provided as either hand-operated or motor-driven. However, since motor 110 and all related components, including reduction gearing, clutch, controls (i.e., controls 394, 396) are all mounted on front top plate 45, a manually operated machine may be converted to motorized operation by the simple substitution of the appropriate top plate 45 containing the motor and related components and utilizing predrilled holes in the left side plate 40 of the machine frame for wiring and line plug. In manual machines, the space within front top plate 45 (see FIG. 4) is unused. Since the machine is being described for automatic operation, further details of the several controls and related mechanisms will be explained as the description proceeds.

Turning now to the automatic step-by-step tray lift mechanisms, and referring primarily to FIGS. 4 to 6, inclusive, pinion shaft 94 extends beyond left side plate 40 where it terminates on a mounting bracket 128 which is fixed to but spaced outwardly of left side plate 40. Fixed to the shaft 94 inwardly of mounting bracket 128 is a tray-lift ratchet wheel 130, which, upon being actuated will lift the tray assembly 50 in step-by-step increments determined by the tooth spacing of ratchet 130. Stepwise motion is imparted to ratchet 130 from cam 108 through cam follower lever 132 and an actuating pawl 134 which is pivotally connected thereto. Cam follower lever 132 is journaled on a mounting shaft 136 fixed to and projecting from lever 132 which carries a follower roller 138 which is constrained against cam 108 by constraining member 140. Additionally, roller 138 is biased against cam 108 by follower-biasing spring 142 which is fixed to follower lever 132 and to mounting bracket 128. Periodically and in accordance with the development of cam 108, actuating pawl 134 advances ratchet wheel 130 for lifting tray assembly 34, step by step, with follower lever 132 turning in the counterclockwise direction about pivot 137. While on its return stroke lever 132 actuates second feed rollers 224, 226 as more fully described below.

It will be appreciated that constraining member cooperates with cam 108 and forms a double constrained cam track therebetween which precludes the follower 132 from turning in the clockwise direction about the follower pivot 136, due to the weight of the tray assembly 34 and paper stack thereon which manifests itself as a clockwise turning force on ratchet wheel 130.

Tray-lift ratchet wheel 130 is also engaged by a holding pawl 144 which is pivoted at 146 on mounting bracket 128. Fixed to the holding pawl 144 is a holding pawl-release lever 148 which is mounted at common pivot 146. Lever 148 is biased to engage holding pawl 144 with ratchet wheel 130 by spring 150 connected to lever 148 and anchored on the side wall 40. Normally, holding pawl 144, due to bias ofspring150, will track movements of the ratchet wheel 130 as it turns in the counterclockwise direction under the influence of actuating pawl 134. Pawl-release lever 148 includes lift finger 1480 which underlies lift tab 134a formed on actuating pawl 134. Thus, upon turning of the pawl-release lever 148 in the clockwise direction about pivot 146 and against the influence of spring 150, not only will holding pawl 144 be released from ratchet wheel 130, but in addition lift finger 148a will engage lift tab 134a to disengage the actuating pawl 134 from ratchet wheel 132. This releases and restores the tray 34 to its lowermost position for reloading. Actuation of the release lever 148 is achieved by release arm 152 which is pivotally connected to lever 148 at pivot 153. Release arm 152 is formed with a finger piece 152a which extends through a confining cutout 40c formed in left side plate 40 at a convenient location above and to the left of the front cover and tray assembly 34 (see FIG. 1). Thus, the user, by simply depressing release finger piece 152a, releases assembly 34 which returns to its lowest position by its own weight.

Provision is also made for manually lifting the tray assembly 34 as seen best in FIG. 6. Mounted on shaft 94, a double-arm pawl lever 154 which carries on its downward arm 1540 an auxiliary pawl 156 which is pivoted at 158. Normally, auxiliary pawl 156 is held out of contact with ratchet wheel 130 by stop 160 fixed to left side plate 40 and abutting extension 156a of pawl 156. The auxiliary pawl 156 is biased toward ratchet wheel 130 by pawl-biasing spring 162, but spring 161 cannot exert its biasing effect as long as extension 156a abuts stop 160. However, when the downward arm 154a of lever 154 is swung in the counterclockwise direction about shaft 94, auxiliary pawl 156 will be lifted to a clearance position in relation to stop 160 and spring 161 will bias the pawl into an operative position in contact with ratchet wheel 130. This is accomplished by the provision of an auxiliary pawl-actuating arm 162 which is pivoted on left side plate 40 at 164 and terminates in a tray-lift finger piece 1620 which extends through arcuate confining cutout 40d in plate 40 and is accessible at a convenient operator location as seen in FIG. 1. Arm 162 is coupled to arm 15411 of lever 154 by connecting link 166 which has a pivotal connection at 168 to arm 162 and a pivotal connection at 170 to the upwardly projecting arm l54b of lever 154. Arm 162 is appropriately biased by spring 172 anchored on left side plate 40. Thus, by depressing finger piece 162a, arm 162 pivots in the clockwise direction about 164 (see FIG. 6) and connecting link 166 in turn pivots lever 154 so that auxiliary actuating pawl 156 is moved into contact with ratchet 130 by spring 161. For each depression of finger piece 162a, there will be a corresponding lifting motion imparted by the motion of pawl 156 to assembly 34 via ratchet wheel 130.

Overlying the tray 50 is a feed roller assembly, generally designated by the reference numeral 174 in FIG. 1, which is seen to include left and right carrier plates 176, 178 (see FIGS. 1, 4 and 17) which are pivoted at 180, 182 on the inner sides of left and right side plates 40, 44, respectively. Carrier lates 176, 178 are interconnected at their upward and forward ends at locations spaced from pivots 180, 182 by a rigid lift bar 184 which extends transversely of the machine and serves to unite carrier plates 176, 178. Extending below and parallel to lift bar 184 is a feed roller shaft 186 of square crosssection which carries a pair of rubber-faced feed rollers 188, 190 disposed inwardly of tray sides 56, 58 and in an operative position to engage successive topmost sheets S of the paper stack S. Feed roller shaft 186 is journaled on the left and right carrier plates 176, 178 by bearings 176a which is self-centering and 178a which is releasable, to allow for operator removal of shaft 186 and replacement of worn rollers 188, 190. Periodically, feed rollers 188, 190 are turned through the appropriate arcuate increment for paper feed (counterclockwise in the diagrammatic showings of FIGS. 2 and 3) by an appropriate drive from shaft 98, and cam 202 described below. Feed roller shaft 186 is coupled (see FIGS. 1 and 17) to its drive through a one-way clutch 192 which is of conventional construction and permits either driving motion to feed rollers 188, 190 or free wheeling in the feeding direction (clockwise in FIG. 17) but blocks turning of the feed rollers in the opposite direction (counterclockwise in FIG. 17). The driving side of clutch 192 is connected to driven gear 194 which is coupled via intermediate gear 196 journalled on carrier plate 178 to driving gear 198 which is connected to shaft 182 which extends (see FIG. 12) to the outer side of the right side plate 44. Shaft 182 has connected thereto a double-arm actuating lever 200 which is actuated by a multi-friction cam 202 secured to the adjacent end of main shaft 98. Cam 202 is engaged by follower roller 204 which is journaled on cam follower lever 206 pivoted on the right side plate 44 at 208. Follower lever 206 is coupled to one arm of the actuating lever 200 by a coupling line 210 which has a pivotal connection at 212 to lever 206 and a pivotal connection at 214 to lever 200. The other arm of actuating lever 200 is connected to followerbiasing spring 215 which is anchored on the right side plate 44. The bias of spring 215 urges coupling link 210 in a direction to engage follower roller 204 against cam 202. Thus, in response to drive of the main cam shaft 98, the requisite periodic motion is imparted to the first set of feed rollers 188, 190 for advancing the topmost sheet of the paper stack toward the duplicating mechanisms 62.

Provision is made for disabling the paper-lift actuating pawl 134 when the tray is at an appropriate level to feed topmost sheets S of the stack S to the duplicating mechanisms. To this end, there is mounted on the left side plate'40, a pawl-lift finger 216 (see FIG. 6) which is pivoted at 218 on left side plate 40 above cutout 40c. Finger 216 is biased by spring 220 anchored on left side plate 40 into a clearance position wherein it does not interfere with the engagement of actuating pawl 134 with sprocket wheel 130. Finger 216 includes a tab 2160 which extends through cutout or window 40c and is in position to be engaged by a depending nose 176a on left side carrier plate 176 (see FIG. 4). As the stack height diminishes, carrier plate 176 of feed roller assembly 176 swings in the counter-clockwise direction about its pivot 180, thus bringing nose 176a into contact with tab 2160. This in turn lowers the pawl-disabling finger 216 (FIG. 6) and permits pawl 134 to engage ratchet wheel 130 to raise the platform 50 to the requisite elevated position for the corresponding stack height. When the stack S is restored to the appropriate position, the feed rollers 188, 190 are raised correspondingly, carrier plate 176 swings in the clockwise direction about pivot and nose 176a swings to a position wherein finger 216 is again rotated to its lifting position in contact with actuating pawl 134 thereby lifting and disabling pawl until it once again becomes necessary to reestablish the stack height.

At the opposite side of the machine (see FIG. 17), there is provided a stop 222 which is positioned to abut carrier plate 178 for the purposes of limiting the motion of the feed roller assembly 174 in the clockwise direction about pivot 182.

Moving further along the paper feed path to the duplicating mechanisms 62, there is provided a second pair of feed rollers 224, 226 (see FIGS. 4 and 19) which are received in corresponding cutouts formed in feed table 60, with feed rollers 224, 226 being faced with rubber or any other appropriate elastomeric material and projecting through the cutouts to contact the bottom of the sheet being fed into duplicating mechanisms 62. The second pair of feed rollers 224, 226 are fixed to a feed roller shaft 228 appropriately journalled on the side plates 40, 44, with the shaft extending into the housings at the left and right of the machine, as seen in FIGS. 5 and 12. Drive is periodically imparted to feed roller shaft 228 from the main shaft 98 of the machine via an adjustable lost-motion mechanism which permits the adjustment of the sheet feed in relation to the duplicating mechanisms 62 to achieve varying registrations between the sheets fed and the stencil or master. Referring specifically to FIGS. 6, 19 and 20, this mechanism is seen to include a driving rack 230 outwardly of left side plate 40 which is pivoted at 137 and includes mounting arm 230a and a segmental rack 230b. Rack 23% engages drive gear 232 on the adjacent end of roller shaft 228. lnwardly of gear 232 and also on the outer side of plate 40 is a coiled biasing spring 234 which is anchored on the machine frame, conveniently at mounting bracket 128. Spring 234 is operatively connected to feed roller 228 to impart a clockwise bias to shaft 228. Rack arm 230a is formed with a follower 230s which is adapted to be engaged by an actuating tab 132a formed on follower lever 132 which tab turns in the clockwise direction about pivot 137 under control of cam 108 on cam shaft 98 (see FIG. 5). Depending upon the position of adjustment of follower 230a on driving rack 230, there will be a lost motion travel of tab 132a relative to follower 2300; and after such lost motion travel, rack segment 23% will be driven in the clockwise direction about pivot 137 to impart a corresponding counterclockwise motion to feed roller shaft 228 and to feed rollers 224, 226 which in turn will impart feeding motion to the underside of sheets of material presented thereto and held thereagainst.

Successive sheets of paper are clamped against the feed rollers 224, 226 by an idler or pinch roller assembly which includes a plurality of pinch rollers 236 (FIG. 4) mounted on a pinch roller shaft 238 journaled coaxially with pivots 180, 182. To feed paper, pinch rollers 236 are rocked on the counterclockwise direction about its pivots downwardly, as shown diagrammatically in FIGS. 2 and 3, they engage the sheet of paper trapped between feed rollers 224, 226 and the pinch rollers. The sheet is fed into duplicating mechanisms 62 in response to actuation of the second feeding rollers 224, 226. The pinch rollers 236 are raised and lowered under control of cam 102, FIGS. 1 and 4, through provision of cam follower roller 240 mounted on follower arm 242, which projects through cutout 40f in side plate 40 and engages cam 102. Follower arm 242 is rigidly connected to the shaft 238 carrying the mounting brackets 244 for the pinch rollers 236.

Projecting above feed table 60 at a location substantially corresponding to the bight of the second feed rollers 224, 226 and the pinch rollers 236 is a paper stop 246 which is pivoted at 248 and biased into its paper-blocking position by spring 250 (see FIG. 4). Stop 246 carries an actuating pin 252 which is in position to be engaged by depending finger 2440 on mounting bracket 244 such that in response to clockwise turning movement of bracket 244 about its pivots 180, 182, and engagement of the pinch rollers 236 with the second feed rollers 224, 226, stop 246 is withdrawn from the feed path to per mit unobstructed paper feed, as seen in FIGS. 2 and 3.

It will be appreciated that the time in the machine cycle that drive is imparted to the second feed rollers 224, 226 in relation to the initiation of any particular machine cycle will determine the position of the leading edge of the paper in relation to the image on the master mounted on the duplicating mechanisms 62. This relative position is controlled by the lost motion travel of actuating tab 132a relative to follower 230C. Adjustment of this lost motion travel is achieved by the mechanisms shown in FIGS. 12, 19 and 20. Referring first to FIG. 12, there is mounted on the outer side of the right side plate 44 an adjustment rack 254 which engages adjustment pinion 256 on the adjacent end of the feed roller shaft 228. Adjustment rack 254 is connected via follower 254a to the spiral cam track 258a of printing height adjustment knob 258 which is mounted on the right side plate 44 and is accessible for adjustment by the operator (see FIG. 1). Adjustment pinion 256 is coupled to the feed roller shaft via a three-part mechanism, FIGS. 19 and 20. The three-part mechanism includes adjustable sleeve 260 fixed to pinion 256 and movable as a unit therewith, intermediate sleeve 262 and follower sleeve 264 fixed to roller shaft 228. Adjustable sleeve 260 includes a radially extending rib 260a which in response to turning of pinion 256 imparts adjustment motion to rib 264a on follower sleeve 264 through the intermediate rib 262a of intermediate sleeve 262. Accordingly, upon appropriate adjustment of knob 258, actuating tab 132a of follower lever 132 will travel a greater or lesser distance before engaging follower 2300 on the driving rack 230 which imparts the feeding motion to the second feed roller shaft 228 and its feed rollers 224, 226.

The final aspect of the paper feeding system includes impression roller 266 (FIG. 4) which is separated from the duplicating mechanisms 62 during the non-printing part of the machine cycle under control of an impression roller blocking assembly 268. Considering first the impression roller 266 and its actuating mechanism, the impression roller 266, which has an appropriate elastomeric face, is mounted on impression roller shaft 270 which in turn is journalled on one arm ofa bell crank 272 which is pivoted at 274 on the machine frame. The other arm of bell crank 272 is connected to a double-arm follower lever 276 which is pivoted at 274 on the outer side of left side plate 40 (see FIG. 6). Lever 276 is connected at pivot 278 to bell crank 274 through window 40g in the left side plate 40 (see FIGS. 4 and 6). Double arm follower lever 276 carries a follower 280 which engages impression roller release cam 104 on main cam shaft 98. As seen in FIG. 5, an impression roller tension spring 282 is mounted by an appropriate bracket 284 on the left side plate 40 and is coupled at mounting tab 2760 to the double arm lever 276. Spring 282 is effective, when released for activation under control of cam follower 280, to turn pivot 278 at the lower end of double arm lever 276 in the clockwise direction (see FIG. 6) to thereby turn the bell crank 274 (see FIG. 4) in the counterclockwise direction to raise the impression roller 266 into contact under pressure with the duplicating mechanism 62. The pressure on the impression roller 266 is determined by the adjustment of coil spring 282, as is generally understood.

Basically, the impression roller 266 includes an inoperative position illustrated in FIG. 4 and shown diagrammatically by the full lines in FIGS. 2 and 3, an operative position 266 against the duplicating mechanisms as shown by the dotted lines in FIG. 3 and an intermediate position 266" established under control of the blocking assembly 268 which, if it does not sense a partially fed sheet, blocks the impression roller 266 from contacting the duplicating mechanisms 62 and picking up an inked impression which would foul the impression roller 266. The blocking assembly 268 which achieves this function includes a sensing finger 268a and a follower lever blocking arm 2681) (see FIG. 4) which are rigid with each other and mounted on a single shaft joumaled on the machine frame at pivot 268c. Blocking arm 26% extends through cutout 40h in the left side plate 40 in position to be contacted by a tab 276b on cam follower arm 276. Thus, as

cam follower arm 276 begins to move from its fully retracted position (shown by the dot-dash showing to the left of the full line illustration in FIG. 6) to the full line illustration, the blocking member 268b will block follower 280 from following cam 104 (as shown by the dot-dash showing at the left of FIG. 6), thereby establishing the blocked position for impression roller 266 wherein the machine rotates, but impression roller 266 is not fouled due to the failure of a sheet to feed.

Duplicating mechanism 62 is in the form of a twin cylinder, silk screen assembly (see FIG. 4), including upper cylinder 286 mounted on upper cylinder shaft 288 and lower cylinder 290 mounted on lower cylinder shaft 292. The twin cylinder assembly 62 carries the usual mechanisms for attaching a stencil master to the silk screen, and for connecting both cylinders with a suitable belt drive for simultaneous rotation of the entire assembly. As seen in FIG. 5, drive is imparted to the lower cylinder shaft 292 by cylinder drive gear 294 which is driven from main drive gear 106 and transferred to the upper cylinder and silk screen in a conventional manner not shown.

Disposed between the upper and lower cylinders 286, 290 are the usual ink-spreading rollers 296, 298 and a removable and replaceable ink distributing tube 300. Reference will now be made to FIGS. 12, 15 and 17 for a description of the mechanisms which axially reciprocate the ink-spreading rollers 296, 298 during machine operation. At the right side of the machine, right side plate 44 is provided with appropriate cutouts 44c, 44d through which roller shafts 296a, 298a project. Shafts are circumferentially grooved and receive respective oscillating arms 302, 304 which are pivoted at 302a, 304a on a common actuating yoke 306. Oscillating arms 302, 304 are biased toward each other and into engagement with shafts 296a, 298a by spring 308, with limits being established by stops on yoke 306. As seen in FIG. 12, yoke 306 is pivoted on the outer side of right side plate 44 by brackets 310, 312 which afford yoke pivots at 314, 316. Yoke 306 is rocked about the coaxial pivots 314, 316 from the main shaft 98 through the provision of a wobbler mechanism which includes (see FIG. 15) angularly disposed wobbler drive discs 318, 320 fixed to shaft 98 and having an oscillating wobbler plate 322 trapped therebetween. Wobbler plate 322 is coupled to a right angle connecting tab 306a on rocker arm 30612 integral with yoke 306 by an appropriate connecting pin 324. Thus, in response to rotation of main shaft 98, reciprocal motion will be imparted to the ink rollers 296, 298, which are simultaneously rotated by cylinders 286, 290. By the simple expedient of spreading the oscillating arms 302, 304 against their bias of spring 308, the in-spreading rollers may be removed.

Reference will now be made to the mechanisms for supplying ink to the ink distributing tube 300, both manually and automatically during machine operation. The ink distributing tube is a conventional unit which includes internal provision for regulating the ink supply to the cylinders 286, 288 through control knob 326. The assembly of ink tube 300, related gears, and knob 326 are all mounted on a common carrier plate 332 which is slidably and removably mounted on a supporting bracket 334 fixed to the outer side of right side plate 44. Additionally, carrier plate 332 supports 21 depending and fixed ink supply tube 336 which connects with the interior of an inksupply cartridge 338 including a can or body 338a and cover 338b serving as a piston. In response to movement of the cover 338b from its upper position when can 338a is full to a lower position contiguous to the bottom of the can, the ink l therein is forced upwardly through ink supply pipe 336 and into cartridge 330. Ink supply tube 336 carries a pressure plate 340. As is generally understood, housing 338:: of cartridge 338 moves upwardly relative to the piston cover 33%. This movement progressively supplies ink to distributing tube 300. To this end, there is provided a rising ink stand 342 which includes cartridge-supporting platform 342a and upstanding carrier 342b appropriately mounted for vertical movement on a mounting bracket 344 fixed to right side plate 44. At its rearward side, the ink stand 342 is provided with a rack 342c which is engaged by elevating pinion 348 on pinion shaft 350.

Pinion shaft 350 also carries elevating ratchet 352 which is engaged by actuating pawl 354 and holding pawl 356. A downward stroke imparted to actuating pawl 354 turns ratchet wheel 352 counterclockwise driving the elevating pinion 348 in the same direction and lifting the cartridge supporting platform 342a for extruding ink from cartridge 338 through ink tube 346 onto the cylinders 286, 290. Holding pawl 356 is pivoted at 356a on right side plate 44 and is urged by gravity into its holding position. Holding pawl 356 includes a disabling tab 3561) which is in the path of upward movement of the pawl-release finger 342d on platform 342 such that the holding pawl 356 is lifted clear of the elevating ratchet 352 when cartridge 338 is empty.

The machine includes systems for imparting the downward actuating stroke to actuating pawl 354, both manually and automatically. The automatic ink-pumping system includes a mechanism which adjusts the frequency of pumping strokes to actuating pawl 354 over a wide range for providing the required amount of ink to the printing mechanisms 62. The adjustment can range from one stroke for ten machine cycles to one stroke for 70 machine cycles, depending upon the ink required for the stencil master used.

The manual ink supply system includes (see FIG. 17) a forwardly extending ink supply lever 358 mounted inwardly of the right side plate 44 of the machine beneath the top cover plate 45 with the lever having a finger tab 3580 in a convenient position at the front of the machine to be depressed by the operator (see FIG. 1) as ink is required. Lever 358 is pivoted at 360 on the inner side of plate 44 and is coupled by a connecting link 362 through cutout 44c to pawl-actuating lever 364 pivoted on the outer side of plate 44 at pivot 366. Connecting link 362 has an override slot 362a at one end to receive actuating pin 358a on lever 358. The opposite end of connecting link 362 is pivotally connected to one arm of the pawl-actuating lever 364 by pin 368, with the other arm of lever 364 being connected at pivot 370 to actuating pawl 354. Spring 372 (FIG. 12) biases actuating pawl 354 against elevating ratchet wheel 352. Thus, upon depressing finger tab 358a, manual ink supply lever 358 turns in the clockwise direction about its pivot 360 and pin 358b bears against the outer end of slot 362a to pull upwardly on connecting link 362. This motion is transmitted via pawl-actuating lever 364 into a downward supply stroke on actuating pawl 354 to elevate ink stand 342a through rotation of ratchet wheel 352.

When pawl-actuating lever 364 is actuated automatically to achieve a supply stroke, override slot 362a effectively isolates the movement of connecting link 362 from supply lever 358 which remains stationary.

The automatic ink-supply system is adjustable by the operator and provides supply strokes to the actuating pawl 354 after any predetermined number of machine cycles and is seen best in FIGS. l2, l5 and 16. A double arm cam follower lever 374 pivoted at 366 and one arm carrying follower roller 376 adjustably engages cam 202 on main shaft 98, and the second arm of lever 374 is connected via a motion input link 378 to a motion-accumulating mechanism 380 which periodically imparts an actuating motion to a motion output link 382. When link 382 is moved, one arm of the ratchet-actuating lever 364 automatically depresses pawl 354 to provide an automatic supply of ink, Such supply strokes are provided after a present number of machine cycles, as determined by the adjustment of a slidable finger piece 384 mounted beneath the front cover 45 of the machine (see FIGS. 1, 12 and 17). Specifically, motion input link 378 is adjusted by a sliding camming plate 386 to control the stroke of lever 374 at pivot 375. Bias spring 388 urges follower 376 toward cam 202 at the adjusted clearance position determined by adjustment of link 378 via a stroke-adjustment tab 378a which extends through cutout 44f on the side plate 44. This adjustment will be described subsequently in conjunction with FIGS. 16 to 18, inclusive. Input link 378 has a pivotal connection at 390 to the drive arm 380a of the motion accumulating mechanism 380 which is a form of oneway clutch which precludes backlash.

Referring now to FIGS. 15 and 16, the motion-accumulating mechanism 380 which receives its input from link 378 via actuating arm 380a includes a fixed central pin 38Gb on which is journalled an inner driving raceway member 3800. Surrounding driving raceway member 380c is an outer raceway member 380d. Plural clutch rollers 3802 are interposed between raceway members 380e, 380d and having appropriate seats 380f on member 380d. In response to clockwise turning motion of the driving raceway member 3800 (see FIG. 16) by upward motion of input link 378, interposed rollers 3802 via seats 380f turn the driven raceway member 380e in the clockwise direction. This in turn imparts incremental motions in the clockwise direction to the diametrically opposed driving pins 380g, 380h which, after of rotation, are coupled in succession to the output motion link 382 at seating cutout 382a. Thus, in response to incremental motions imparted to motion input link 378 from cam follower 376 (which incremental motions are indicated by the multiple small clockwise arrows in FIG. 16), the driving pins 380g, 380k periodically come into link cutout 382a to pull the link 382 through an actuating stroke which is sufficient to impart a supply stroke to actuating link 354 for the requisite automatic supply motion to ratchet wheel 352.

In order to assure that the motion-accumulating mechanism 380 will accurately accumulate the incremental clockwise motions imparted thereto, any appreciable backlash or counterclockwise motion must be avoided. Backlash would tend to cancel the small incremental accumulations during each machine cycle, and therefore a holding raceway member 380i is provided surrounding the driven raceway member 380d. Member 380i is fixed by mounting arm 380j and anchor pin 380k to the right side plate 44. interposed between the driven raceway member 380d and the stationary holding raceway member 380i are plural clutch rollers 3801 which bear against seats 380m on member 380i and oppositely arranged to seats 380f. Thus, driving motion is accumulated in the mechanism 380 and passed to driven raceway member 380d and thence to the motion output link 382 in response to clockwise input, with all counterclockwise motion effectively blocked by the counteracting rollers 380l which wedge against the stationary seats 380m on holding raceway member 380i.

From the foregoing, it will be appreciated that the total stroke of motion input link 378 is determined by the throw of cam 202 and the adjusted position of follower roller 376 relative thereto. Thus, if follower roller 376 moved quite close to cam 202, it will contact a rising cam surface sooner and provide a greater upward thrust to motion input link 378. Link 378 is biased by spring 388 to move cam follower 376 in the counterclockwise direction about pivot 366 (see FIG. 12) into a limit position close to cam 202 determined by the bottom wall of cutoff 44f. As link 378 is moved upwardly by adjustments of tab 378a, less and less of the total throw of the cam 202 is transmitted via follower 376 to motion input link 378 and the clockwise incremental motions to arm 380a correspondingly decrease. Accordingly, it will take a greater number of machine cycles and rotations of cam 202 to accumulate sufficient motion in mechanism 380 to drive output link 382 between its full and broken line positions which correspond to one step of the elevating ratchet 352 to provide a predetermined supply of ink into the ink distributing tube 300. As previously pointed out, adjustment of tab 378a is accomplished by the slidable inking control finger piece 384 on the front top plate 45 of the machine. Referring now to FIGS. 1, l7 and 18, the inking control finger piece 384 is seen to be mounted for side to side sliding movement by a mounting block 384a which extends into cutout 45a on top plate 45. Connected to finger piece 384 is a camming plate 386 having an angularly disposed camming ledge 386a. Camming ledge 3860 is engaged by cam follower 389 which is pivoted at 391a to rock about a substantially horizontal axis in response to side to side displacement of cam plate 386. Cam follower bracket 389 includes a cam follower arm 389a (see FIG. 17) which engages the cam ledge 386a and an output arm 38% (see FIG.

18) disposed in spaced parallel relation to the follower arm 38% and substantially at right angles thereto in position to lie beneath and engage adjustment tab 3780 on motion input link 378. As finger piece 384 is pushed to the right (see FIG. 1), follower cam 389a will turn in the counterclockwise direction about pivot 3910 (see FIG. 17) to lower arm 38% and permit tab 378a to drop under bias of spring 388. This in turn brings cam follower roller 376 closure to its actuating cam 202 and thereby utilizes a greater portion of the cam throw, and provides a more rapid accumulation of rotary motion in mechanism 380 which is translated into more frequent pumping action of the automatic ink-supply system. Correspondingly, adjustment of finger piece toward the left in FIG. 1 utilizes less of the cam throw and a corresponding slower motion accumulation and a less frequent pumping action.

Disposed above the finger piece 384 on the top plate 45 is a motor control panel 392 which includes a motor on-off pushbutton 394 and a speed control knob 396 controlling the usual rheostat (see FIG. 18). Motor pushbutton 394 turns the motor 110 on and off through a conventional circuit and switch. Additionally, pushbutton plunger 394a is coupled to the handle or crank 100 on main shaft 98. As seen best in FIG. 15, handle or crank 100 includes an inwardly facing coupling collar 1000 which is provided with diametrically opposed cutouts which receive corresponding pins 98b on shaft 98. Outward displacement of handle 100 on shaft 98 (to the left in FIG. decouples handles from shaft 98. This is accomplished in advance of energization of the motor 110 to assure that the handle 100 will not rotate during motorized operation. As seen in FIG. 18, plunger 394a engages crank-disengaging double arm lever 400 which is pivoted by appropriate bracketing at 402 and is connected to a pull rod 404 at pivot 406. Pull rod extends through cutout 44 in the right side plate 44 and engages a double arm actuating lever 408 (see FIGS. 12 and 15) which is provided at 316 and includes arm 4080 which displaces the handle 100 in advance of motor turn-on. Provision is made intermediate lever 408 and push rod 404 for achieving adjustment of the position of lever 408 to the extent required to assure complete handle disengagement in response to rocking motion oflever 408.

Reference will now to be made to FIGS. 12 to 14, inclusive, for a description of the remaining controls of the machine which, as seen, are mounted on the front wall of the right side cover 42 and include, from top to bottom, a paper feed on pushbutton 410, paper feed off pushbutton 412 and an impression roller release pushbutton 414. Considering first the impression roller release pushbutton 414, it will be recalled that impression roller blocking assembly 268 controls the release of the impression roller 226 through sensing finger 268a mounted on shaft 268s. As paper is fed, it lifts finger 268a and permits release of impression roller 266. Pushbutton 414 overcomes this control and permits finger 268a to be released through link 416 to actuating arm 418 on shaft 268: at the outer side of right side plate 44 (see FIG. 12).

The function of the feed on button 410 and the feed off button 412 is most easily understood by reference to FIG. 13 which shows the onoff control in the on position and FIG. 14 which shows it in the off" position. The function of the on-off control is either to enable paper feed by permitting cam follower 204 to engage cam 202 (see FIGS. 12 and 13) or to lock follower 204 and its follower arm 206 in a clearance position relative to cam 202 (see FIG. 14). Normally, cam follower lever 206 is biased by spring 215 in a direction to engage follower roller 204 against cam 202.

For operator convenience, three ways are provided for feed turn-off; manually by pushing button 412 as indicated by arrow 0 in FIG. 14, automatically in response to countdown of a counter 438 as indicated by arrow 0 and automatically when the paper supply in tray 50 is exhausted as signalled by the position of slide block 92b and indicated by arrow 0 First considering the sequence pursuant to which the machine is manually turned on, and referring to FIG. 14, it is seen that the on pushbutton 410 includes the usual spring biased plunger 410a biased by coil spring 41% and bearing against button-actuated lever 420. Lever 420 is also in position to be engaged by the plunger 4120 of off pushbutton 412 which likewise appropriately is biased by coil spring 412b. Button-actuated lever 420 is connected via spring 424 to paper feed disabling latch 426 which is pivoted at 428 on right side plate 44. Latch 426 includes a latch seat 4260 which engages a latch piece 206a on follower lever 206 to lock the follower lever in the clearance position relative to cam 202. Disposed beneath latch piece 426 is a stop 430 which is fixed to the right side plate 44. Normally, latch piece 426 is biased against stop 430 by spring 432 which is anchored in any appropriate fashion. Latch piece 426 is released from its latched position as established by its stop 430 and its spring 432 by pushing on arm 420a of lever 420 to turn arm 420b in the clockwise direction about pivot 422 to exert a pull via spring 424 on latch 426 to swing latch seat 426a in the counterclockwise direction about pivot 428 which releases lever 206, as may be appreciated by progressively inspecting FIGS. 14 and 13.

Provision is made for latching button-actuated lever 420 in the on" position so that it is only necessary that the operator momentarily depress the on pushbutton 410. This is accomplished by the provision of an intermediate latch and release plate 434 which is pivoted at 436 and includes latch seat 4340 which engages latch piece 4200 on lever 420, the latched posi tion being shown in FIG. 13. Plate 434 includes cam part 434b which is positioned to be engaged by plunger 412a of the off pushbutton (see the full and broken lines shown in FIG. 14) to rock latch and release plate 434 to a position wherein lever 420 is released from its latch position, whereupon spring 432 is effective to swing paper feed disabling latch 426 to its latched position shown in FIG. 14. Thus, the machine may be turned on by pushing button 410 and turned off by pushing button 412.

In addition to manual shut off as indicated by directional arrow 0 the machine is shut off by countdown of the counter 438 which is of conventional construction and includes the usual setting dials 438a which may be set to the desired number of copies (illustrated as 35"). After countdown (see the setting in FIG. 14), the counter 438 turns the machine off. Countdown input to counter 438 is normally derived in response to each machine cycle as represented by one rotation of the main shaft 98 by the provision on Wobbler plate 322 of a counter-actuating arm 322a (see FIGS. 12 and 15) which engages counter actuator 438b which is normally biased to its forward position by bias spring 438c. Each time actuator 438b is pushed forwardly against the bias of its spring (to the left in FIG. 15), the indicated remainder is reduced by one. When the counter 438 reaches to zero, its output shaft 438d is turned to rock counter output arm 438a in the counter-clockwise direction, when viewed from the front of the machine (away from side plate 44 in FIGS. 13 and 14). Positioned adjacent the counter output ann 438e is a counter release lever 440 which is pivoted at 436 and is biased into the FIG. 13 position by spring 442. When lever 440 is depressed by the output arm 438e of counter 438, as indicated by arrow 0 in FIG. 14, it swings plate 434 in its unlatching direction above pivot 436 to release latch at 434a, and 4206 such that button-actuated lever 420 swings in the direction to release its latching force on latch piece 426 whereupon the paper feed is turned off.

Provision is made for disabling counter actuation by blocking counter actuating arm 3220 through blocking arm 426b which is formed integrally with latch piece 426 and is in the counter blocking position when the machine is turned off as seen in FIG. 13. In response to counterclockwise turning of latch piece 426, as the machine is turned on, blocking arm 426b moves to a clearance position wherein counter actuating arm 322a is free to contact counter actuator 438b to initiate the countdown.

The third turnoff method, indicated by directional arrow 0 is achieved by mounting a double arm paper height sensing lever 444 at pivot 428. Lever 444 has a follower 444a overlying block 92b and an actuating arm 444b which carries a push plate 444C which engages adjustable follower screw 4340 on plate 434. Thus, when slide block 92b approaches the limit of guideway 44b, when paper stack is depleted as seen by progressively inspecting FIGS. 14 and 13, lever 444 rocks about pivot 428 to swingv push plate 4440 in the counterclockwise direction which in turn pivots latching releasing plate 434 to release button-actuated lever 420 to disengage paper feed.

What is claimed is:

1. In a printing machine, a feed tray for supporting a stack of sheets including adjustable left and right side guides which are movable laterally relative to each other in accordance with the width of said stack, left and right corner separators mounted for movement with and laterally relative to said left and right side guides respectively, said left and right corner separators being movable in unison with and in response to adjustment of said left and right side guides respectively, and actuating means for simultaneously adjusting said left and right corner separators laterally relative to said left and right side guides when the latter are in an adjusted position for obtaining independent adjustment of said left and right corner separators in various adjusted positions of said left and right side guides to provide varying degrees of interference at the corners of successive uppermost sheets of said stack as said sheets are fed into said printing machine.

2. In a printing machine according to claim 1, a single manual control for said actuating means.

3. In a printing machine according to claim 1, stabilizing means interconnected between and coordinating said left and right corner separators.

4. In a printing machine according to claim 3, said stabilizing means including a freely floating stabilizing bar slidably engaging said left and right corner separators and arranged to permit said separators to move toward and away from each other under control of said left and right side guides.

5. In a printing machine according to claim 1, an abutment wall extending transversely of said machine and positioned forwardly of said feed tray in the direction of feed, said left and right comer separators being loosely mounted on said abutment wall and being adapted to bear against the left and right forward corners of said stack.

6. In a printing machine according to claim 1, left and right carrier plates movable with said left and right side guides and left and right actuating levers mounted on said left and right carrier plates and respectively coupled to said left and right corner separators.

7. In a printing machine according to claim 6, said actuating means including a common actuating member movable to impart adjustments to both said left and right actuating levers independent of said left and right side guides, said actuating member remaining stationary when said left and right side guides are being adjusted and said actuating levers moving relative to said actuating member during such adjustments.

8. In a printing machine according to claim 1, said actuating means being constructed and arranged to move said left and right corner separators in opposite directions relative to each other and symmetrically relative to said side guides of said feed tray.

9. In a printing machine, a feed tray for supporting a stack of sheets including a bottom wall and left and right side guides mounted on said bottom wall for movement relative to each other for overall adjustment in accordance with the width of said stack, a stack-abutment wall extending across the front end of said feed tray against which the front end of said stack abuts, left and right corner separators loosely mounted on said stack-abutment wall and adapted to bear against the corresponding corners of the topmost sheet of said stack, connecting means operatively connecting said left and right corner separators to said left and right side guides respectively for overall adjustment therewith and independent adjustment means operatively connected to said left and right corner separators for adjusting same relative to, but independently of, said left and right side guides to obtain varying degrees of interference at the topmost sheet of said stack.

10. In a printing machine according to claim 9, stabilizing means interconnecting said left and right corner separators and constructed and arranged to preclude skewing of said separators and to permit said separators to move relative to each other during both overall and independent adjustment.

11. In a printing machine according to claim 9, said stabilizing means including a stabilizing bar extending transversely of said machine behind said stack-abutment wall and slidably connected to said left and right comer separators.

12. In a printing machine according to claim 9, said connecting means including left and right carriers operatively coupled to and movable with said left and right side guides and left and right coupling means on said left and right carriers operatively connected to said left and right corner separators for both coordinated and independent adjustment thereof with respect to said left and right side guides.

13. In a printing machine according to claim 12, said left and right coupling means including left and right actuating levers pivotally mounted on said left and right carriers and remaining stationary and serving as motion-transmitting means during said overall adjustment.

14. In a printing machine according to claim 12, said independent adjustment means including said actuating levers and a common actuating member movably mounted below said bottom wall and connected to said actuating levers for pivoting the same to impart independent adjustments to said left and right corner separators.

15. In a printing machine, a main drive, a paper tray assembly and lifting mechanisms for raising said tray assembly in discrete steps to present the topmost sheet of a stack of paper thereon for feed to said printing machine, said lifting mechanisms including a tray-lift ratchet, a first actuating pawl normally engaging said ratchet and actuated from said main drive to impart indexing motion to said ratchet, a second actuating pawl movable into engagement with said ratchet and normally disposed in a retracted position relative thereto, manually operable means for moving said second actuating pawl into engagement with said ratchet and for then imparting indexing motion to said ratchet, a holding pawl normally engaging said ratchet, a pawl-release means operable to disengage both said first actuating pawl and said holding pawl from said ratchet to permit said tray assembly to be lowered into a loading position.

16. In a printing machine according to claim 15, further manually operable means for actuating said pawl-release means.

17. In a printing machine according to claim 16, said pawlrelease means including a pivoted pawl-release lever operatively connected to said holding pawl, actuating means including a finger piece for pivoting said pawl-release lever to disengage said holding awl from said ratchet and means on said pawl-release lever operable to release said first actuating pawl from said lever in response to pivoting of said pawl-release lever.

18. In a printing machine according to claim 15, said manually operable means including means mounting said second actuating pawl for movement into engagement with said ratchet and actuating means including a finger piece for both engaging and actuating said second actuating pawl.

19. In a printing machine including a main drive and a paper-feeding mechanism having actuating means operable from said main shaft to initiate paper feed, a control for selectively coupling and decoupling said actuating means of said paper feeding mechanism from said main drive, said control including a latch normally arranged to hold said actuating means in a decoupled position from said main drive, a first manual control operatively connected to said latch for disengaging same from said actuating means whereby said actuating means is coupled to said main drive, a second manual control operatively connected to said latch for engaging same with 

1. In a printing machine, a feed tray for supporting a stack of sheets including adjustable left and right side guides which are movable laterally relative to each other in accordance with the width of said Stack, left and right corner separators mounted for movement with and laterally relative to said left and right side guides respectively, said left and right corner separators being movable in unison with and in response to adjustment of said left and right side guides respectively, and actuating means for simultaneously adjusting said left and right corner separators laterally relative to said left and right side guides when the latter are in an adjusted position for obtaining independent adjustment of said left and right corner separators in various adjusted positions of said left and right side guides to provide varying degrees of interference at the corners of successive uppermost sheets of said stack as said sheets are fed into said printing machine.
 2. In a printing machine according to claim 1, a single manual control for said actuating means.
 3. In a printing machine according to claim 1, stabilizing means interconnected between and coordinating said left and right corner separators.
 4. In a printing machine according to claim 3, said stabilizing means including a freely floating stabilizing bar slidably engaging said left and right corner separators and arranged to permit said separators to move toward and away from each other under control of said left and right side guides.
 5. In a printing machine according to claim 1, an abutment wall extending transversely of said machine and positioned forwardly of said feed tray in the direction of feed, said left and right corner separators being loosely mounted on said abutment wall and being adapted to bear against the left and right forward corners of said stack.
 6. In a printing machine according to claim 1, left and right carrier plates movable with said left and right side guides and left and right actuating levers mounted on said left and right carrier plates and respectively coupled to said left and right corner separators.
 7. In a printing machine according to claim 6, said actuating means including a common actuating member movable to impart adjustments to both said left and right actuating levers independent of said left and right side guides, said actuating member remaining stationary when said left and right side guides are being adjusted and said actuating levers moving relative to said actuating member during such adjustments.
 8. In a printing machine according to claim 1, said actuating means being constructed and arranged to move said left and right corner separators in opposite directions relative to each other and symmetrically relative to said side guides of said feed tray.
 9. In a printing machine, a feed tray for supporting a stack of sheets including a bottom wall and left and right side guides mounted on said bottom wall for movement relative to each other for overall adjustment in accordance with the width of said stack, a stack-abutment wall extending across the front end of said feed tray against which the front end of said stacks abuts, left and right corner separators loosely mounted on said stack-abutment wall and adapted to bear against the corresponding corners of the topmost sheet of said stack, connecting means operatively connecting said left and right corner separators to said left and right side guides respectively for overall adjustment therewith and independent adjustment means operatively connected to said left and right corner separators for adjusting same relative to, but independently of, said left and right side guides to obtain varying degrees of interference at the topmost sheet of said stack.
 10. In a printing machine according to claim 9, stabilizing means interconnecting said left and right corner separators and constructed and arranged to preclude skewing of said separators and to permit said separators to move relative to each other during both overall and independent adjustment.
 11. In a printing machine according to claim 9, said stabilizing means including a stabilizing bar extending transversely of said machine behind said stack-abutment wall and sLidably connected to said left and right corner separators.
 12. In a printing machine according to claim 9, said connecting means including left and right carriers operatively coupled to and movable with said left and right side guides and left and right coupling means on said left and right carriers operatively connected to said left and right corner separators for both coordinated and independent adjustment thereof with respect to said left and right side guides.
 13. In a printing machine according to claim 12, said left and right coupling means including left and right actuating levers pivotally mounted on said left and right carriers and remaining stationary and serving as motion-transmitting means during said overall adjustment.
 14. In a printing machine according to claim 12, said independent adjustment means including said actuating levers and a common actuating member movably mounted below said bottom wall and connected to said actuating levers for pivoting the same to impart independent adjustments to said left and right corner separators.
 15. In a printing machine, a main drive, a paper tray assembly and lifting mechanisms for raising said tray assembly in discrete steps to present the topmost sheet of a stack of paper thereon for feed to said printing machine, said lifting mechanisms including a tray-lift ratchet, a first actuating pawl normally engaging said ratchet and actuated from said main drive to impart indexing motion to said ratchet, a second actuating pawl movable into engagement with said ratchet and normally disposed in a retracted position relative thereto, manually operable means for moving said second actuating pawl into engagement with said ratchet and for then imparting indexing motion to said ratchet, a holding pawl normally engaging said ratchet, a pawl-release means operable to disengage both said first actuating pawl and said holding pawl from said ratchet to permit said tray assembly to be lowered into a loading position.
 16. In a printing machine according to claim 15, further manually operable means for actuating said pawl-release means.
 17. In a printing machine according to claim 16, said pawl-release means including a pivoted pawl-release lever operatively connected to said holding pawl, actuating means including a finger piece for pivoting said pawl-release lever to disengage said holding pawl from said ratchet and means on said pawl-release lever operable to release said first actuating pawl from said lever in response to pivoting of said pawl-release lever.
 18. In a printing machine according to claim 15, said manually operable means including means mounting said second actuating pawl for movement into engagement with said ratchet and actuating means including a finger piece for both engaging and actuating said second actuating pawl.
 19. In a printing machine including a main drive and a paper-feeding mechanism having actuating means operable from said main shaft to initiate paper feed, a control for selectively coupling and decoupling said actuating means of said paper feeding mechanism from said main drive, said control including a latch normally arranged to hold said actuating means in a decoupled position from said main drive, a first manual control operatively connected to said latch for disengaging same from said actuating means whereby said actuating means is coupled to said main drive, a second manual control operatively connected to said latch for engaging same with said actuating means whereby said actuating means is decoupled from said main drive, a counter and means responsive to operation of said counter and operatively connected to said latch for engaging same with said actuating means to decouple same from said main drive.
 20. A printing machine according to claim 19 including a movable paper-supply tray and means responsive to movement of said paper-supply tray into a predetermined position to engage said latch with said actuating means to decouple same from said main drive.
 21. In a printIng machine, printing mechanisms, paper-feeding mechanisms for said printing mechanisms including first and second sets of feed rollers, a main drive including a main drive shaft, a first cam on said main drive shaft, first connecting means including a first cam follower and a first one-way clutch for imparting first intermittent feeding motion to said first set of feed rollers, a second cam on said main drive shaft and second connecting means including a second cam follower and a second one-way clutch for imparting second intermittent feeding motion to said second set of feeding rollers in a lagging timed relation to said first motion whereby paper is advanced by said first set of feed rollers into said second set of feed rollers and then picked up and advanced by said second set of feed rollers into said printing mechanisms.
 22. In a printing machine according to claim 21, said first and second cams being disposed symmetrically of said machine and at opposite sides of said paper-feeding and printing mechanisms.
 23. In a printing machine according to claim 21, said second set of feed rollers including a drive roller and a cooperating pinch roller movable relative thereto and means including a third cam on said main drive shaft for moving said pinch roller into cooperating relation with said drive roller in timed relation to driving of said first and second sets of feed rollers.
 24. In a printing machine according to claim 23, a paper stop positioned in operative relation to said second set of feed rollers and normally blocking paper feed thereto and means controlled from said third cam for removing said paper stop in timed relation to movement of said pinch roller into cooperating relation with said drive roller.
 25. In a printing machine, a movable paper tray assembly and lifting mechanism for raising said tray assembly in discrete steps, a paper-feeding mechanism including at least one set of feed rollers, a main drive including a main drive shaft and a cam thereon, connecting means including a cam follower operable from said cam and operatively connected to said set of feed rollers for imparting feeding motion thereto and further connecting means operatively connected to said follower for actuating said lifting mechanism.
 26. In a printing machine according to claim 25, said cam including a follower track having opposed constraining walls such that said follower is constrained against movement out of engagement with said cam due to the weight of paper on said movable tray assembly. 